FR2767172A1 - TORSION SHOCK ABSORBER - Google Patents

Abstract

Shock absorber (10) comprising a first element (12) and a second element (14) connected by a spring installation (20). The installation (20) comprises at least one damping device (38) with at least one damping spring (40). The elements (12, 14) carry supports (36) for the support elements (42). The element (12) has a sliding surface (34). In the event of relative rotation between the elements (12, 14), the support element (42) is driven along the sliding surface (34) and is pushed against this surface. A grease chamber (94) is provided at the surface of the sliding surface (34) -

Description

The present invention relates to a shock absorber

  torsional oscillations, in particular to dampen oscillations,

  torsion states produced in the transmission line of a motor vehicle comprising: - a first damping element, - a second damping element which can rotate about an axis of rotation relative to the first damping element,

  - a first shock-absorbing spring installation which

  ple the first and the second damping element for the transmission of the torque, - the first installation with damping spring comprising

  at least one shock absorbing spring device extending

  approximately in the peripheral direction with at least one damping spring, - on a damping element of the first and second damping element, there are support means for at least one damping spring device, against which at least one shock absorbing spring device at

  its respective end zones, substantially in the di-

  peripheral rection, by a support element provided in each end and, - on at least one damping element for each support element, there is a sliding surface along which the corresponding support element can slide in the peripheral direction, and in addition on the other damping element among the first and the second damping element, means are provided

  associated with each support element by the

  which, on the occasion of a relative movement between the first and the second damping element, the associated bearing element can be pushed for a sliding movement along

  of the associated sliding surface on a damping element

  weaver and towards the sliding surface.

  Such a torsional oscillation damper is known for example according to document DE 195 44 832 A1. In this known torsional oscillation damper, the first and the second damping element are at least concentric

  by zone and are staged radially. The sliding surfaces

  for the respective support elements are formed on

  inner periphery surface segments rotated inwardly on the first damper; the drive means are formed by a design of the contour of the outer peripheral surface of the second damping element. In particular, the second element

  The shock absorber is in the shape of a polygon, so that, considering it in the peripheral direction, there are bosses projecting radially outwards forming ramps 10 which allow, during the relative movement between the first and the second shock absorbing element, '' train the associated supporting elements. In this drive, the support elements slide radially outward on the sliding surfaces. Between the drive means made in the form of a ramp and the sliding surface, a

  corner in which by spring effect damped springs

  respective sors, are pushed the supporting elements which have a corner configuration if necessary. The second damping element pushes with its external peripheral surface, that is to say the radially external zones protruding in the form of a ramp, the support elements against the respective sliding surface to generate a friction force effect there. . There is thus a damping effect combined by the respective damping springs and the force

friction thus generated.

  In the particular embodiment described above

  above for this known torsional oscillation damper, the problem is that due to the sliding movement with friction along the sliding surfaces, there is wear which creates the risk of seizing or blocking of the support elements and thus an increase in the risk of rupture of the guide elements of the support elements in the event of a bending load.

  The present invention therefore aims to develop

  lopper a torsional oscillation damper reducing the risk of wear in the area of components that rub against one

on the other.

  To this end, the invention relates to a torsional oscillation damper, characterized in that at least at

  At the level of the sliding surface, at least one grease chamber is provided which is sealed radially outward and contains grease.

  As a result, in the problematic area in which there is a sliding and friction effect, the penetration of the fat between the components rubbing one

  on the other reduces the risk of seizure or blockage and this

wear him.

  In a torsional oscillation damper of the

  type defined above, we also have the difficulty that by

  particular in the region of the resonance frequency of a

  transmission or torsion oscillator damper, the torsional oscillations generated may not be sufficiently damped. This is why, it is proposed according to the invention that at least one damping spring

  is provided at least by zone in the grease chamber and

is in the fat.

  This means that in addition to the damping effect by spring compression and creation of friction force.

  We participate in the damping by the movement of the damping spring and also of the support elements in the grease. This is of particular interest in the area of resonant frequencies to achieve much better damping. According to another advantageous characteristic of the invention, the grease chamber is formed by:

  - a first segment in the form of a disk extending essentially-

  radially and belonging to the first damped element

weaver,

  - a cylindrical segment extending essentially axially-

  ment, and adjacent to the first disc-shaped segment at its radially outer region,

  - a second segment preferably in the form of a ring of the

  that extending essentially radially as a dis-

  that, on the cylindrical segment by its end opposite the first disc-shaped segment, adjacent to its radially outer end zone, in

  extending essentially radially.

  Advantageously, the sliding surface is produced in the form of a cylindrical segment at its inner peripheral surface.

  To avoid that, for example, at rest,

  say when no centrifugal force acts on the grease, the latter can move radially inwards and out of the grease chamber, it is provided that the second damping element is rotatably mounted by a bearing device on the first damping element and / or a component

  integrally connected thereto and in that the bearing device forms a first sealing device for the grease chamber with respect to an axial side of the second damping element.

  It is further advantageous that it includes in-

  be a second sealing device provided between the second disc-shaped segment and the second damping element,

on its other axial side.

  Significant savings are achieved when the torsional oscillation damper according to the invention is produced, since the first disc-shaped segment and / or the cylindrical segment are preferably integral with the first disc-shaped segment. and / or the second segment in

  disc shape and / or the second damping element, in

  taking at least one piece of prefabricated sheet metal

rence by deep drawing.

  It should be noted that in this context of the present invention, one or more of the characteristics of

  the invention can be taken independently.

  According to a torsional oscillation damper

  type known according to document DE-195 44 832 Ai, we have another

  be difficult, because in operation, for example in the event of reverse thrust or sudden release of the vehicle's friction clutch, maximum torques are reached which could be transmitted by the torsional oscillation damper and damage components of the

drive system.

  This is why, according to other characteristics of the present invention, it is planned to develop

  the torsional oscillation damper of the type defined above

  above so as to include an overload protection installation to absorb the maximum torques at

  transmitted by the torsional oscillation damper.

  The overload protection installation comprises at least one friction clutch. Such provisions

  friction clutch devices have a certain slip or friction torque defined for a certain torque range, i.e. up to friction torque, the devices can transmit torque without it there is slippage between the components of the device; in case of

  overshoot of this couple, there is sliding and thus

  tion of the torque transmitted by this friction clutch device

tion.

  The overload protection installation

  ges may include for example a clutch device to

  friction acting between the two components of the first element

  shock absorber or / and a friction clutch

  acting between two components of the second damping element.

  According to another advantageous characteristic, at least one sliding clutch device comprising an annular sliding element mounted to rotate on the element

  shock absorber and attacking it by friction, and this element

  annular has the sliding surface and the

support means.

  As a variant or in addition, the installation of

  overload protection includes a general installation

  generating a friction force acting between the first and the second damping element or the components integral with them, and generating as the relative angle of rotation increases, an increasing friction force between the

  first and second damping element.

  In the case of such friction devices acting

  Generally in traction in known overload protection installations, provision may also be made for the installation generating a friction force not to generate

  practically no frictional force up to an angle of ro-

  relative tation constituting a threshold and when exceeding this relative angle of rotation constituting a threshold, it generates an essentially constant friction force or increasing with the relative angle of rotation.

  According to the torsional oscillation damper known from document DE-195 44 832 Ai, the second damping element is mounted for rotation on the first damper or a component integrally connected to the latter. When such a torsional oscillation damper is integrated in a transmission line, for example in the form of a two-mass flywheel of a friction clutch, there is the difficulty that due to the axial offset between the input axis and the output axis or due to a nutation movement, at least one of the axes produces greater wear at the level of the bearing of the two damping elements. To avoid such

  wear, it is provided according to another aspect of the present in-

  vention, a torsional oscillation damper of the above type

  which is made for mounting the bearing so

  that the first and the second damping element can act

  make at least one movement with respect to the other

  tilting and / or sliding movement in the direction

radial tion.

  When in such torsional oscillation dampers, there are nutation movements mentioned above

  for at least one tree element and thus the cushioning element

  weaver integral with it, these damping elements can

  wind tilt one against the other or slide without in the area of the bearing of the two damping elements,

  does not meet undue hardship.

  The expression "tilting movement" means

  here also that at least one of the damping elements can tilt relative to the geometric axis of rotation and takes

  thus an angle different from 90 with respect to this axis of ro-

  geometric tation. It is clear that this expression includes

  also the simultaneous tilting of the two damped elements

  sors if necessary also when they are parallel.

  The expression sliding movement in the radial direction means here a relative sliding movement independent of the respective tilting state of the two damping elements with respect to each other and which can thus be moved relative to their arrangement of

  base It is clear that according to the tilting state, this

  Radial sliding can also contain a

axial sliding component.

  One can for example provide that the bearing device comprises at least one deformable bearing component

  elastically preferably a bearing component 10.

  Advantageously, the bearing device comprises bearing components acting between the first

  and the second damping element essentially in the di-

  axial rection and a component acting between the first and

  the second damping element essentially in the direction

radial tion.

  To make tipping even easier, it is

  proposed that the second damping element include an over-

  convex bearing face, to come into abutment against the provision

bearing sitive.

  Under these conditions, it is further advantageous that the drive means comprise on the other element

  shock absorber each time a convex drive surface.

  The known torsional oscillation damper is

  DE-195 44 832 A1 also provides for each shock absorbing spring device, a shock absorbing spring for

  the load range. This design with a volume of res-

  relatively reduced lot results in an insufficient damping function for the different frequencies

torsional oscillation.

  According to another characteristic of the invention, it is thus proposed to develop a torsional oscillation damper of the type defined above so that at least one spring damper device comprises at

  at least two shock absorbing springs and at least the two

  shock absorber spells are supported by their end zone

  sine against an intermediate element which can move

  in the peripheral direction with respect to a damping element

weaver.

  Thanks to such an embodiment of the cushioning device

  spring weaver with two shock-absorbing springs connected in series, a significantly greater suspension volume is obtained and thus much better oscillation damping characteristic. The intermediate element may include a sliding element sliding on the sliding surface. For

  that in such an embodiment of the oscillating damper

  torsion, the damping behavior is practically not influenced by the intermediate element, it

  it is proposed that the intermediate element is essential mobile-

  frictionless in the peripheral direction compared to

wear to a damping element.

  For this, we can foresee for example that more

  a number of spring damping devices distributed in an essentially equidistant manner in the peripheral direction and the respective intermediate elements for the various spring damping devices are mounted on a ring

  of support rotating relative to a damping element.

  The existence of several shock-absorbing spring devices with peripheral interval and their cooperation with the intermediate elements provided each time on the support ring creates a self-centered device in which the intermediate ring is held without support to any other

  damping component, in a certain and practical way-

  independent of the state of rotation, in its relatively

diale.

  To predict appropriate depreciation behavior

  suitable for all load states or rotational speed, it is provided according to another advantageous characteristic of the present invention that at least one other spring damper installation which is mounted so as to cooperate in

  series with the first installation of spring shock absorbers.

  This spring damping installation can for example be an idling spring damping installation which acts in response to very low torques and goes to rest when a limit value is exceeded, either before or after the first installation. spring damping which has already provided the damping function. Likewise, it is possible that at least the other spring damping installation comprises at least one spring damper device with at least one damping spring. This installation comprises a damping means for high loads acting when large torques are induced and the first spring damping installation then practically no longer acts for

  dampen rotational oscillations. The existence of a heavy-duty damping facility and an idle damping facility is possible in conjunction with the first spring-loaded damping facility.

  There is a particularly simple and space-saving embodiment if at least one other spring damper installation comprises a torque transmission coupling between two components rotating one relative to

  the other of the first damping element and / or between two

  posants rotating relative to each other of the second damping element. With the torsional oscillation damper according to the invention, it is for example possible to associate a clutch with

  friction with a clutch disc. In this case, it is pos-

  sible that the clutch disc has at least one other spring damping installation acting between two components rotating relative to each other of the clutch disc. So you can effectively use the volume

  available in the clutch disc area.

  So that when couples are applied which

  exceed the torque damping range of installations

  respective damping springs and risk damaging these spring damping installations or the shock absorbing springs fitted to them, it is proposed that the first shock absorbing spring installation and / or the

  if necessary at least one other spring-loaded installation

  weaver comprise end stop means for limiting the relative angle of rotation of the rotating components

relative to each other.

  According to the torsional oscillation damper known according to document DE-195 44 832 Ai, the support elements in the radial direction are held essentially

  between the first and the second damping element. That if-

  gnifie that it is possible to have between the support elements and the second damping element, a friction contact in the event of relative rotation of the two damping elements. This is particularly troublesome and delicate if the second element

  shock absorber constitutes a flywheel element of an em-

  motor vehicle friction clutch. This element of your-

  The inertia lant then receives the heat from the clutch and must evacuate it. Due to the risk of friction contact between the second damping element and the support elements, it is possible to

  thus accidentally inducing heat in the elements

  supporting elements. As these support elements are produced for reasons of cost and adjustment of the friction force

  preferably at the sliding surface

  plastic, the resulting heat can damage or

destroy these supporting elements.

  To avoid this, it is provided according to another advantageous characteristic in the case of a shock absorber

  torsional oscillations of the type defined above in the-

  which the sliding surfaces are provided on a cylindrical segment extending essentially in the axial direction, with its inner peripheral surface, to form a

  damping element and furthermore between a damping element

  sor and each support element, there is a fixing means

  axial acting for the support element.

  In particular, a damping device with res-

  sort includes at least two shock-absorbing springs, the two neighboring end zones of which move relative to

  one of the damping elements, in the peripheral direction

  preferably based on the sliding intermediate element on the sliding surface and axial fixing means-intermediate element are provided for

the intermediate element.

  l For example, the means of axial fixing of the support element and / or where appropriate the means of axial fixing of the intermediate element can be provided on an element of the sliding surface or of the support element. or of the intermediate element with a peripheral groove and the other element may include a projecting area

  of fixing to take in the peripheral groove.

  A very space-saving arrangement in the di-

  axial rection of the torsional oscillation damper

  lon the invention is obtained if a damping element comprises a disc-shaped segment which extends essentially

  in the radial direction and which is connected in a ra-

  dialement external to a cylinder-shaped segment and is provided on a first axial side of each support element and the other damping element comprises a disk-shaped segment extending essentially in the radial direction and which is in a radially outer area of

  the other axial side of each support element.

  In such an embodiment, the disc-shaped segment which extends radially in one of the damping elements, the disc-shaped segment corresponding opposite to the other axial side of the element is thus removed. support of a damping element, so that it

there is no grease chamber.

  In such an embodiment, it is also possible to perform a cooling function, for example grease without having to give it up, if it is as proposed, between the disc-shaped segment of the other damping element.

  and each support element, there is a certain axial distance.

  Thanks to this predetermined axial distance, we create an ori-

  inlet for cooling air, so that the heat given off at the second damping element is

  can quickly transfer and dispose of it to other components

  health. As already indicated, it is necessary in a drive system, to have different damping characteristics depending on the speed and the torque,

  to have an appropriate damping function for each

  that torque range. According to another aspect of the present invention, it is proposed for this purpose to develop a torsional oscillation damper of the type defined above so

  that at least one damping spring provides for a characteristic

  variable spring tick as a function of relative rotation

  increasing between a first and a second damping element.

  This can be facilitated for example if at least

  a damping spring present in the basic state, a confi-

  guration approximately rectilinear and in the assembled state and

  the unloaded state of the torsional oscillation damper

  it is more strongly prestressed in the area of

  fate located radially inside that in the area of

  spring located radially on the outside.

  In such an arrangement, it is therefore first of all essential that the radially inner zone of a

  damping spring acts under the effect of its strongest pre-

  constraint. As compression increases, the area

  external dialing is more and more prestressed, so that from the spring characteristics of the radially internal zone and the radially external zone of the shock-absorbing spring, one obtains a characteristic of compound spring, variable gradually with the state

compression.

  To make maximum use of the damping capacity of at least one damping spring, it is proposed that at least one damping spring is prestressed

  essentially identical, in the essential state-

  compressed and as much as possible in its radially outer zone

  and in its radially inner zone.

  This means that at least one damping spring present in its essentially maximum state of compression,

  an essentially rectilinear configuration.

  The spring characteristic which varies according to the state of rotation can for example be adjusted in that at least one damping spring bears at least in one of its end zones against a bearing surface, the zone of which radially outer support is offset from

  its radially inner support zone, in the direction

  device, for at least one of the end zones of

  minus a 40k shock spring stroke.

  The offset can be such that in the no load state

  or in a lower state of charge, essentially only-

  of the area radially inside the damped spring

  sor is in support and that only when a determined torque is exceeded, the area radially inside also comes to bear against the support area radially outside the support surface and thus participates in

the damping effect.

  In order to be able to increase the spring volume in the case of a torsional oscillation damper having a construction of the type defined above, it is proposed according to another advantageous characteristic of the invention that at least one damping spring is preferably pre-bent and extending from the peripheral direction and that means

  radial support are provided which support at least one

  shock absorber spell in its outer radial zone of prefe

  along its entire length, radially outward.

  The shock absorbing spring which extends in the direction

  peripheral tion can have a length such that it occupies

  practically 180 and thus gives an extremely large spring volume

* very important. If the sliding surface is the means

  radial support, no additional components are required

for that.

  So that in the area of the radial support of at least

  minus a damping spring, it prevents wear, it is

  that the radial support means have a treated support path. It should be noted that the treated support track is also advantageous in combination with the support elements, so that for example even for the elements

  support, the sliding surface may include a

treated support face.

  According to other characteristics of the invention: - an overload protection installation to absorb the maximum torques to be transmitted by the shock absorber

torsional oscillations.

  - the overload protection installation comprises at least one sliding clutch device. - the overload protection installation includes a friction clutch device acting between two

  components of the first damping element and / or a device

  friction clutch acting between two components

of the second damping element.

  the bearing device is made so that the first and the second damping element make it possible to carry out at least

  a tilting movement and / or a sliding movement

in the radial direction.

  - the bearing device comprises at least one component of

  elastically deformable bearing preferably components

plain bearing sants.

  - the intermediate element includes a sliding element

  sliding on the sliding surface.

  - a friction clutch is associated with the torsion damper oscillator with a clutch disc, this

  clutch disc with at least one other installation

  spring damping cooperating between two components

  health likely to rotate relative to each other and

belonging to the clutch disc.

  - axial fixing means-support element act in-

  be a damping element and each support element.

  - The means of axial fixing of the support element and / or the

  where appropriate the means of axial fixing of the element

  intermediate include on an element of the surface of

  sliding and supporting element or an intermediate element

  diary, a peripheral groove and on each other element

  ment, a protruding fixing area penetrating the

peripheral groove.

  - between the disc-shaped segment of the other damping element and each support element, there is a distance

predetermined axial.

  - at least one damping spring has a characteristic

  as variable spring with relative rotation increasing

  health between the first and second damping element.

  - The radial support means are constituted by a sliding surface. - The radial support means comprise a treated support path. - at least one shock-absorbing spring device comprises a

single damping spring.

  So that the spring volume of at least one

  positive spring shock absorber is maximum, it is proposed

  that it comprises a single damping spring. This

  puts to maximum use the peripheral range provided

  for a spring damping device.

  The torsional oscillation damper according to the invention can for example be produced so that: the support element has a substantially wedge-shaped shape

  which narrows in the peripheral direction and a seg-

  The sliding surface applied against the sliding surface of a damping piece for the support element forms a first corner surface and a driving surface provided for pressing against the respective driving means. a second corner surface and - the drive means comprise a surface area

  shaped as a drive ramp at least per segment,

  parallel to each drive surface.

  To avoid a concentration of load when sliding the respective support element along the sliding surface, it is proposed that the sliding surface segment has a surface contour at least approximately adapted to the peripheral contour of the

sliding surface.

  The present invention will be described below from

  in more detail using different embodiments

  sation shown schematically in the accompanying drawings, in which: - Figure 1 is a cross section in the form of a segment of a torsional oscillation damper corresponding to a first embodiment of the present invention, - Figure 2 is a sectional view along line II-II of Figure 1, - Figure 3 is a view corresponding to that of Figure 2 along a section line III-III of Figure 1, - Figure 4 is a view corresponding to that of FIG. 2 of another embodiment of a torsional oscillation damper according to the invention in connection with a friction clutch of a motor vehicle,

  - Figure 5 is a partial sectional view of another va-

  laughing embodiment of a torsional oscillation damper according to the invention,

  - Figure 6 is a partial longitudinal section of an au-

  a variant embodiment of a torsional oscillation damper according to the invention with a grease chamber, FIG. 7 is a view corresponding to that of FIG. 6 of another variant embodiment of an installation creating a friction force having a drag effect, - Figure 8 is a view corresponding to that of Figure 6 of another embodiment of a torsional oscillation damper with damping elements capable of performing movements of nutation,

  - Figure 9 is a partial longitudinal section of an au-

  tre embodiment of a torsional oscillation damper according to the invention with a friction clutch as a means of overload protection, - Figure 10 is a partial cross section of a

  torsional oscillation damper representing different

  rents embodiments of intermediate elements for spring damping devices, - Figure 11 is a perspective view of a support element,

  - Figure 12 is a partial longitudinal section shown

  feeling the embodiment of the right intermediate element of FIG. 10, FIG. 13 is a view corresponding to FIG. 12 of an alternative embodiment of the intermediate element and of a support ring which carries it,

  - Figure 14 is a perspective view of the support ring

  port of FIG. 13 with the corresponding intermediate elements, FIG. 15 shows different embodiments of spring damping devices of the oscillation damper of

torsion according to the invention.

  Figures 1 to 3 show a first mode of

  realization of a torsional oscillation damper 10 se-

  lon the invention. The torsional oscillation damper 10

  comprises a first damping element 12 which can for example

  ple be connected in a radially inner zone to a vi-

  lebrequin not shown belonging to an internal combustion engine so that during the drive by the internal combustion engine, it forms the input part. The torsional oscillation damper 10 also comprises a second damping element 14 mounted by a bearing 16 on an axial projection 18 integrally connected to the first damping element

  12 while being able to rotate with respect to the first element 12. In-

  be the first and the second damping element 12, 14, there is a first damping spring installation 20 described later as well as a second damping spring installation 22. This means that the first damping spring installation 20 and the second installation shock absorber spring 22 connects the first shock absorber element 12 to the

  second damping element 14 for transmitting the torque.

  It should be noted that the expression "element" as used here does not relate to single pieces, but as shown in particular in the figures, these elements

  can consist of several parts.

  The first damping element 12 comprises a

  first segment or segment of cover panel 24 es-

  substantially radially extending disc-like; this

  segment 24 is connected radially inside with the city

  brequin or can be connected to it. Radially outside, the first disc-shaped segment 24 is

  continues with a cylindrical segment 26 extending essentially-

  in the axial direction. The cylindrical or cylindrical type segment 26 is connected to a second disc-shaped segment 28, by its end axially distant from the first disc-shaped segment 24; the connection is made radially to the outside, for example by screws or the like. The second disc-shaped segment extends radially inwards and forms, for example, a second overlapping segment. In the radially inward end region 10, the second disc-shaped segment or segment of cover plate 28 is connected integrally by

  several bolts or similar means, distributed in the peripheral direction, at the first segment in the form of a disc or segment of overlapping sheet metal 24. The peripheral-internal surface 32 of the cylindrical segment 26 comprises a surface

  sliding face 34. In the peripheral direction, the first disc-shaped segment 24 and the second disc-shaped segment 28 have spaced apart supporting parts 36 to extend towards each other, axially from the disc-shaped segments. The support elements 36 can for example be riveted to the respective disc-shaped segments, be welded or similarly fixed. In addition, the support pieces can occupy the entire axial gap between the two disc-shaped segments 24, 28, i.e. they can be made in one

  room. The support pieces 36 serve as supports for devices

  shock-absorbing spring elements 38 of the first shock-absorbing spring installation 20; the first shock-absorbing spring installation 20 comprises several shock-absorbing devices

  spring 38 distributed successively in the peripheral direction

  rique and extending practically in this peri-

  spherical. Each damper device 38 according to the embodiment shown in Figures 1 to 3 consists of two damper springs 40 or includes them. The end zones of the shock-absorbing spring devices 38 located

  in the peripheral direction build on the

  shock absorber spells 40 by support elements 42 which will be described below against the support pieces 36 so that the various shock absorber springs 40 are slightly prestressed. By their neighboring end zones, the damping springs 40 are supported by a shoe 44 constituting an intermediate element. Both shoe 44 and the elements

  support 42 can be moved as described above

  after during the transmission of the torque by the torsional oscillation damper, with the sliding surface segments 46, 48, along the sliding surfaces 34

  on the first damping element 12 in the peri- direction

  spherical. During such a sliding of one of the elements

  support 42 of the shock-absorbing spring device 38, this element

  support leg 42 is raised relative to the associated support piece 36.

  The second damping element 14 comprises an element

  hub 50 ment connected integrally in a radial zone

  interior with a mass piece 52 constituting by

  example the flywheel of a friction clutch.

  The hub element 50 comprises, as can be seen in particular from FIGS. 2 and 3, a first hub part 58 and a second hub part 54 substantially in the form of a fork; this second part is coupled by studs 56 to the flywheel 52. The second hub part 54, the cross section of which corresponds substantially to a fork, forms cover sheet segments 60, 62 between which is located a radial flange 64 of the first part hub 58. The radial flange 64 as well as the cover sheet segments 60, 62 comprise

  spring windows 66, 68, 70 including

  bare control edges for shock absorber springs 72

  of the second shock-absorbing spring installation 22.

  According to the figures, the first shock-absorbing spring installation 20 and the second spring-loaded installation

  shock absorber 22 cooperate in series.

  To transmit a torque between the first element

  ment damper 12 and the second damper element 14, that is to say between the hub part 58 of the second damper element 14, the first hub part 58 has a contour with an outer peripheral surface without symmetry of

  rotation. Each time in the peripheral end zones

  that of the spring-loaded damping devices 38, there are corresponding segments of the first hub part 58 constituting ramp-shaped zones 74 projecting radially5 projecting outwards; so as it appears for example in the view of figure 1, in the peripheral zone

  from the first hub part 58 opposite the shoe 44, the radius of the first hub part 58 increases in the two peripheral directions towards the ramp-shaped surface areas 74 to their top. This means that

  corresponding the radial distance between the sliding surface

  ment 34 and the outer peripheral surface of the first hub part 58 decreases at the level of the surfaces in the form of

ramp 74.

  As further appears in Figure 1, the support elements 42 have a section essentially wedge-shaped. Thus, the sliding surface segments 46 have a contour respectively adapted to one of the surfaces of

  sliding 34, that is to say that their contour corresponds ap-

  proximally to a contour in the shape of a circle segment.

  Correspondingly, the support elements 42 have sur-

  drive faces 76 radially inside which, when pressed against the ramp-shaped surface areas 74 are at least substantially parallel in places to the areas

  ramp surface 74. Due to the reduction in the

  radial tance already mentioned above between the sur-

  ramp-shaped face and sliding surface 34 by

  relation to the peripheral end zones of each device

  shock absorbing spring 38, there is thus a wedge-shaped torque transmission device. This means that, according to FIG. 1, the first hub part 56 rotates clockwise and thus the second damping element 14 rotates relative to the first element

  shock absorber 12, the ramp-shaped surface area 74

  presented below in FIG. 1, drives the support element 42 which is associated with it, in the peripheral direction, against the spring action developed by the shock absorber spring 40. In this case, the two shock absorber springs 40

  assembled in series are compressed almost in the same way

  niere. The shoe 44 thus also moves in the direction

  peripheral device, clockwise.

  But as at the level of the ramp-shaped surface area 44, the distance relative to the sliding surface 34 decreases and the damping springs 40 push

  the support element 42 provided at the bottom left, in this inter-

  valley which tapers into a wedge shape, the cooperation of the ramp-shaped surface area 74 with the drive surface 76 pushes the support element 42 radially

  outwards against the sliding surface 34. This ef-

  pressure fet directed radially outward increases due to the compression of the shock-absorbing springs 40 with

  increasing the relative angle of rotation between the first

  first shock absorber part 12 and the second shock absorber part 14, so that in the support zone, between the

  sliding surface 34 and the sliding surface segment

  smoothing 46 of the respective support element 42, this creates a

  increasing friction force with the relative angle of rotation

  tive and thus a damping effect. This damping effect can also be increased if the area of

  sliding 34 does not have a circular configuration.

  For example, this surface can have a confi-

  guration whose radius decreases from the peripheral end zones of each shock-absorbing spring device 38 towards its central zone. This means that the first part

  of hub 58 drives the support element 42 and the latter

  smooth with its bearing surface area 42 along a surface

  sliding face 34 as it approaches the interior, so that the radial distance between the ramp-shaped surface area 74 and the sliding surface 34 decreases more and more and that the wedge effect and the force of friction

generated increase.

  The serial arrangement of the first installation

  tion with shock absorber spring 20 and the second installation with shock absorber spring 22 allows stepped shock absorber operation as a function of the load. It is for example possible to produce the first installation with a shock-absorbing spring 20 with shock-absorbing springs 40 as load shock-absorbers and the second installation with a shock-absorbing spring 22

  with shock absorbing springs 72 as shock absorbers

  slow. This means that in the practically unloaded state, when a torque transmitted by the vibration damper of

  twist 10 is not yet sufficient to compress the res-

  shock absorbers 40, torque variations are absorbed

  gaped or damped by the relative rotation of the first and second hub parts 58, 54 one with respect to

  the other and the compression thus created of the damped springs

  seurs 72. In this case also, we can have a functioning-

  staged so that first of all only certain shock-absorbing springs 72 act and only when

  reaches a certain relative angle of rotation between the first

  and the second hub part 58, 54 that there is another displacement of the shock-absorbing springs 72. This is shown

  in Figure 1 in that for example for the damped spring

  seur 72 shown on the right, the spring windows 68, 70 of the cover plate segments 62, 60 have substantially the same peripheral extension as the spring window 66 of the first hub part 58, so that at the slightest twist between the first and second hub parts 58,

  54, the damping spring 72 provided in these resistor windows

fate acts.

  For the shock-absorbing spring 72 shown at the bottom left of FIG. 1, each of the associated windows 68,

  cover sheet segments 62, 60 has an extension

  peripheral zion larger than the spring window cor-

  correspondent 66 in the first hub part 58; so what

  only when a certain angle of rotation is reached

  lative between the first and the second hub part 58, 54 that this damping spring acts. The selection of the number of respective shock absorbing springs and the peripheral extension of the spring windows depend on the desired damping characteristics. The layout can also

  be such that the respective spring windows of the seg-

  cover sheet elements 60, 62 have a perimeter length

  more reduced and the associated spring window 70

  in the first hub part has a greater peripheral length. To prevent that when reaching an angle of ro-

  determined relative tation, that is to say when a certain torque is induced, the shock absorber springs of the various shock absorber spring installations 22, 20 are damaged, provision is made for overload protection installations for these shock absorber springs in the form stop. For example in FIGS. 1 and 2, studs 30 connecting the first and the second disc-shaped segment 24, 28 of the first damping element 12, radially inside, constitute an overload protection installation or a stop for the first shock-absorbing spring installation 20. The

  studs 30 pass through holes extending in the direction

  peripheral device, i.e. oblong holes 78 made

  in the cover plate segments 62, 60 of the

  this hub part 54. In addition, the studs 30 pass through a passage orifice 80 in the form of an oblong hole, extending in the peripheral direction of the radial flange 64 of the first hub part 58. The peripheral extension of

  the through hole 80 is smaller than the perimeter extension

  through the orifices 78. For a certain rotation

  relative position between the first damping element 12 and the second damping element 14 or first hub part 58, the studs bear against the end segments

  peripherals of the respective passage openings 80 prohibited

  sant thus any continuation of the relative rotation between the first damping element 12 and the first hub portion 58. The relative angle of rotation for which such an abutment occurs avoiding any continuation of the relative rotation is preferably chosen so that '' at this time

  shock absorber springs 40 are not yet fully com-

  award-winning, that is, are not blocked.

  FIG. 3 shows an alternative embodiment of an overload protection installation for the first installation with shock-absorbing spring 20. The second hub part has internal peripheral toothing

  82 which engages with peripheral play in a den-

  outer peripheral structure 84 complementary to the segment 18 extending axially. Between the second damper part 54 and the segment 18 and thus the first damper element 12, because of the teeth 82, 84 which engage, there is a

  some angular rotation. But when you reach the limits

  tes, the respective teeth 82, 84 come into abutment and in-

  terrify any other relative rotation.

  It should be noted that an overload protection installation can also be produced by the bearing of segments of the support element 42 or of the shoe 44. As at least the support elements 42, due to their sliding characteristics, are preferably made of plastic at least at their sliding surfaces 34, if these elements provided the

  overload protection function, this could

damage these items.

  The second shock-absorbing spring installation 22 also includes an overload protection installation. As has been described in connection with FIG. 3 for the first shock-absorbing spring installation 20, by the internal peripheral toothing 86 produced on the radial flange 64 which comes to take in a complementary external peripheral toothing 88 of the second shock-absorbing part 54 with peripheral play. This means that for a certain relative rotation between the first and the

  second part of the hub 58, 54, any further rotation

  tion is prohibited by the coming into abutment of the teeth 86, 88.

  To provide for an additional amortization effect

  shut up, independent of the state of relative rotation, it is

  provided a friction installation in the form of a year-

  friction ring 90 pushed by a prestressed spring, for example a Belleville spring 92 in the axial direction against the second hub part 54. The Belleville spring 92 then bears against the end region radially at

  the inside of the second disc-shaped segment 28 of the first

mier damping element 12.

  Additionally, as shown in Figures 2 and 3,

  the first disc-shaped segment 24, the cylindrical segment

  drique 26 and the second disc-shaped segment 28 of the first

  mier damping element 12 define a grease chamber 94 which contains a lubricating agent for example grease 96 or the like. When the torsional oscillation damper is rotated around the axis of rotation A, the

  grease 96 is placed in the area radially outside. This-

  it creates a lubrication function for the movement of the

  smoothing of the support elements 42 along the trajectory

  sliding 34. Due to the relative surface pressure

  important between these components, this avoids in particular in the area of heavy loads, that the elements

  support 42 do not seize. It is clear that the lubricating agent

  fiant 96 and the surfaces sliding each time between them, i.e. the sliding surface 34 and the sliding surface segments 46 are tuned by their friction property to generate at the same time the friction damping force , desired, depending on the angle

  relative rotation. In addition, lubricant 96 in the

  which the damped springs at least partially dip

  seurs 40 of the first shock-absorbing spring installation

  , creates a damping function, because these springs

  weavers 40 by deforming must move a fluid of

  high viscosity. Thanks to the lubricating agent 96 which thus creates

  if a damping effect and the realization of the provisions

  shock absorber spring 38 shown in Figures 1-3,

  with two shock absorbing springs 40 connected in series,

  reads a damping characteristic which above all avoids the creation of resonance oscillations in the transmission line and which at the same time ensures remarkable oscillation damping in other ranges of oscillation frequencies. In particular, proportional depreciation

  at speed, thanks to the lubricant 96 reduces the con-

  trapped during load changes, i.e. in case of

sudden reversals of the couple.

  It should be noted that the agent room

  lubricant (or grease chamber) 94 is sealed

  inwardly dialed in by the bearing 16 on the one hand and on the other by the friction ring 90 and the Belleville spring 92; the chamber is filled via an opening 98 which can be closed. The grease chamber 94 can be filled with a lubricating agent so that it arrives radially inside up to at the second shock-absorbing spring installation 22. This also makes it possible to lubricate the second shock-absorbing spring installation 22 and for this second shock-absorbing spring installation 22, there will be an additional damping function linked to the movement of the

  different components in a viscous fluid.

  Figure 4 shows an alternative embodiment of

  the torsional oscillation damper according to the invention.

  The components of the torsional oscillation damper shown in Figure 4 and which correspond by their shape

  and their function to the components already described with the aid of FIGS. 1 to 3, bear the same references supplemented by the suffix "a". In the following, for FIG. 4, we limit ourselves mainly to the differences between this form of realization.

sation and that described above.

  The first damper 12a also comprises a first segment or segment of covering sheet 24a, extending substantially in the radial direction and connected radially to the outside to a cylindrical segment 26; this

  set can be made in one piece. On the axia- side

* opposite the cylindrical segment 26, there is no se-

  cond sheet metal segment or disc-shaped segment. Furthermore, the mass part 52a of the second damping element 14a is opposite the respective support elements 42a or of the damping spring devices 38a and their

  shock absorber springs 40a directly with a certain

  tance D. The mass part 52a is fixed in rotation to the hub part 100a produced here in a single

  piece by several screws 56a; the hub part 100a comprises

  carries in its area radially outside a sur-

  face 74a in the form of a ramp. It should be noted that the ramp-shaped surface areas 74a can be made in one piece with the hub part 10Oa; he can

  also be separate elements or with a seg-

  separate annular ment which is then connected integrally in rotation to the hub portion 10Oa. This also applies to the various embodiments described above and those below of the torsional oscillation damper according to the invention. In addition, the hub part 10Oa is rotatably mounted on the first damping element 12a by a bearing

axial 117a.

  As shown in FIG. 4, a friction clutch 102a of a motor vehicle, known per se, is connected to the mass part or flywheel 52a. The clutch

  comprises a casing 104a connected by several screws located ra-

  dialing outside, at the mass part 52a. In known manner, a force accumulator is supported on the casing 104a for example in the form of a membrane spring 106a so that in the engaged state, it presses a plate 108a in the direction of the flywheel 52a. Under these conditions, between the pressure plate 108a and the flywheel 52a, there is a clutch disc.

  11Oa fitted with two friction linings 112a for the trans-

  couple's mission. This clutch disc 110a has at its

  tower two discs or pieces of sheet metal 114a, 116a. The garnitu-

  friction res 112a are connected to the disc part

  114a; the two disc parts 114a, 116a are connected so-

  lidarily to each other by studs not shown.

  Between the two disc parts 114a, 116a, there is a segment

  annular hub 120a connected integrally in rotation to the input shaft 118a of the gearbox. This hub ring segment is connected to the disc parts 114a, 116a

  by a shock-absorbing spring installation 122a having

  several shock absorbing springs 124a for the transmission of the torque. The shock-absorbing spring installation 122a has a construction known per se; she can in particular have the

  same structure as the second damped spring installation

  sor 22 shown in Figures 1 to 3. In the embodiment

  In FIG. 4, the shock-absorbing spring installation 122a can perform the role of an idle shock absorber and at

  the clutched state for the clutch 102a, it is again connected

  purchased as standard on the first damped spring installation

  sister 20a. In this case the idle damping function is transposed from the area of the second damping element 14a to the area of the clutch disc 110a. This allows for example a realization in one piece not shown in Figure 4 for the entire second part

  shock absorber 14, for example in the form of a connected piece

  lée. Due to the reduction in the number of parts, this

  also translates into lower cost.

  It should be noted that the series mounting of more

  in various shock-absorbing spring installations, as in the embodiment in FIG. 1, the value is lowered

  (c) and a better decoupling of the oscillations is thus obtained

  tions. The respective load range in which the different

  Annuities with damping spring acting can be determined according to the damping characteristics of the desired oscillations. It is also possible that

  the shock-absorbing spring installation 122a as well as the

  conde damping installation 22 of Figure 1 form

  a shock absorber with high load which acts only when the capa-

  depreciation city of the first installation

  depreciation 20a is already used up. In addition, it is re-

  note that the various damped spring installations

  can be performed so that their active ranges

  respective overlap or are directly adjacent.

  In addition, it is also possible to connect in series in the clutch disc 11Oa, several shock-absorbing spring installations, for example a damping installation under load and an idling damping installation, mounted in series. Editing a disc

  rigid, non-damping clutch is also possible.

  The torsional oscillation damper 10a according to FIG. 4 is of the dry type, that is to say that the range in which the support elements 42a and the first damped spring installation 20a are provided, is open d 'a side

  axial namely on the side of the flywheel 52a. To allow

  to dissipate the heat received during the

  operation of the clutch 102a in particular at the level of the

  lant of inertia 52a, an air gap 126a is provided.

  But since there is no provision for a second disc-shaped segment at the level of the first damping element 12a, there is a

  guide projection 128a in the peripheral direction

  rique on the cylinder-shaped segment 26a to come to take in guide cavities 130a complementary support elements 42a. This produces an axial blocking for the support elements 42a. This prevents that in operation,

  these support elements cannot move axially and come to bear against the flywheel 52a. As already in-

  dique, the support elements 42a are preferably made of plastic, so that contact with the flywheel 52a

  heated by the operation of the clutch could

  damaging the support elements 42a. It should be noted that the guide projection 128a does not necessarily occupy the entire peripheral direction and it suffices in particular that it exists in the zones in which the support elements 42a flow. The embodiment shown in Figure 4 is simpler and less expensive to manufacture due to the removal of a component of the first damping element 12a namely the second segment in the form of a disc and the corresponding manufacturing step. The damping effect of the grease or of a lubricant, thus eliminated, can also be compensated for by the shock-absorbing spring installation.

122a in the clutch disc.

  To further adjust the damping behavior of the oscillations, in the embodiment of FIG. 4, it is also possible to produce the hub element 100a of the second damping element 14a

  as in the embodiment of FIG. 1, that is to say

  say also to provide a damped spring installation

sister in this area.

  Figure 5 shows another alternative embodiment.

  tion of a torsional oscillation damper according to the invention. The components correspond to those of the figures

  1 to 3 with the addition of the suffix "c".

  The torsional oscillation damper of the fi-

  gure 5 is distinguished in particular by the production of the first damping element 12c. This has an effect at the level of the cylinder-shaped segment 26c, a ring 130c extending in the peripheral direction and which is pre-

  ference closed. This 130c ring is applied with prec-

  tows against the inner peripheral surface 128c of the cylinder-shaped segment 26c. This prestressing can be generated on the one hand by the dimensioning of the ring 130c and on the other hand by the action of the force of the various shock-absorbing spring devices 38c on the radial deformations 132c of the ring 130c. The deformations 132c form the support pieces 36c for the support elements 46c. Thus by the action of the force exerted by the different springs

  shock absorbers 40c, substantially in the peripheral direction

  that the radial deformations 142c in the form of a ramp are pushed radially outwards and thus against the inner peripheral surface 128c of the cylindrical segment 26c. The sliding surface 34c of the support elements 46c

  is the inner peripheral surface of the ring 130c.

  Thanks to the ring 130c which is sliding in the peripheral direction relative to the cylindrical segment 26c, there is a kind of friction clutch which on the one hand thanks to the prestressing effect already indicated and to the configuration of surface of the ring 130c and on the other hand thanks to the segment

  cylindrical 126c, has a coefficient of sliding

  completed; this slip coefficient corresponds to the maximum torque that this clutch coefficient can transmit to

  friction without sliding by these different components. When-

  that the maximum transmissible torque is exceeded, which occurs for example when the torque passes through a maximum, in the event of a sudden reversal of thrust, the sliding clutch slides, that is to say that the ring 130c is moves with all these components which follow it in the direction of the force, with respect to the cylindrical segment 26c. The passage thus created in a sliding state with friction reduces the sliding torque, which makes it possible to effectively absorb the spikes

  of couple. When the torque to be transmitted decreases again

  calf, this removes the sliding state and the state of money

  tion which is restored between the ring 130c and the cylindrical segment 26c allows normal transmission of the torque. Besides the advantage already mentioned of the amortization

  maximum torques, the embodiment according to FIG. 5 offers the advantage of not having to connect different parts

  support other components as is the case in the embodiment of Figures 1 to 3. It should nevertheless be noted that even in the embodiments of fi-10 gures 1 to 4 and in the embodiments described later

  laughing, the different support pieces can be

  performed for example by axial deformations or deformations

  radial formations of the first damping element.

  Figure 6 shows another alternative embodiment.

  tion of the torsional oscillation damper according to

  the invention. The components which correspond to those already de-

  described in Figures 1 to 3 by their design or their function

  bear the same references with the letter "d" as a suffix.

  In the following, the description will be limited to the various

  sentials relative to the embodiments of FIGS. 1 to 3. The embodiment of FIG. 6 also comprises a first installation with damping spring 20d acting between the first and the second damping element 12d, 14d. The shock-absorbing spring installation 20d comprises several shock-absorbing springs 40d which are supported by support elements not shown in the figure on support pieces 36d in the peripheral direction. A hub element 50d has radially outside the zones of

  ramp-shaped surface 74d for driving elements

  supporting elements, in the peripheral direction. The element of

  hub 50d is, as shown in Figure 6, formed essential-

  Lement of two disc elements forming hubs 140d, 142d joined radially inside by screws 56d to the flywheel 52d. In the area of the connection of the elements of

  hub disc 140d, 142d flywheel 52d, parts

  those which form the components of this second damped element

  seur 14d are mounted by means of a first bearing 144d acting essentially in the axial direction and a second bearing 146d acting both in the radial direction and in the axial direction, in a rotary manner on the first damping element 12d or segment 18d. The first and second bearings 144d, 146d are formed essentially by plain bearing rings. The plain bearing ring which constitutes the first bearing 144d has several axial holes 148d in which the heads of the screws can take

  56d and thus drive this first level 144d in the direction

  peripheral tion. In addition, the first bearing 144d includes

  a cavity 150d through which grease 96d can be inserted

  troduit in the grease chamber 94d through the orifice 98d. The second bearing 146d has a cross section similar to an L and it is prestressed by a force accumulator, for example a Belleville spring 152d in the direction of

  first bearing 144d thereby holding the second damping element

  weaver 14d in the axial direction.

  According to Figure 6, the two disc elements forming hubs 140d, 142d are made of simple sheet metal parts formed for example by a deep drawing process. Due to the symmetrical embodiment, it suffices to form a single type of hub disc elements which are used both for the element 140d and for the element 142d. Compared to the production of the hub disc element 50d in cast iron, due to the elimination of machining jobs by removing complicated shavings, for example in the area in which the ramp surfaces are formed

  74d, this variant offers considerable cost advantages.

  wheat. It should be noted that for example also the first damping element 12d can be constituted by sheets formed by deep drawing. This is how, for example, the first 24d disc-shaped segment can be produced.

  as a sheet metal part in one piece with the cylinder segment

  drique 26d by a deep drawing operation. On the way

  laughing, it is also possible to manufacture these separately

  two parts, then join them together by welding, riveting, screw-

  wise or others. The production of one of these pieces as castings and the other as sheet metal is also

  a possible solution. The grease chamber 94d is sealed

  read from an axial side, namely from the left side according to FIG. 6 by the bearing 144d. On the other axial side, namely on the right side according to FIG. 6, the sealing is ensured by a sealing flange 154d applied against the hub element 142d and which is subjected to the prestressing of a friction ring 156d which rests radially on the outside against the second disc-shaped segment 28d. The sealing flange 154d and the friction ring 156d are rotationally connected in their bearing zone, so that the hub element 50d and the sealing flange 154d rotating with the latter rotate the l sealing ring 156d which thus rubs against the second disc-shaped segment 28d. In the same way, it is possible

  to generate a friction force by relative rotation in

  be the hub element 50d and the sealing flange 154d.

  This friction can participate in the damping of oscillations-

  regardless of the relative angle of rotation.

  We also note in Figure 6 that the steering wheel

  52d inertia has 160d ventilation holes

  due to the interval 126d between the first damping element 12d and the second damping element 14d

  and thus allowing rapid removal of the ab-

  absorbed by the torsional oscillation damper 10d.

  It should be noted once again that the realization of the grease chamber 94d and the grease 96d which it contains offers the advantage of ensuring a damping proportional to the speed and of greasing the place where slip movements occur. . In particular in the case of engines with a reduced number of cylinders, for example 3 or 4 cylinder engines, this improves the damping in the range of the resonant frequency which is significantly above the ignition frequency of

  engine. It is therefore possible to delete another element.

  spring damping ment for example at

the hub element 50d.

  Figure 7 shows a development of

  the torsional oscillation damper of Figure 6 in particular

  at the level of the mounting of the two damping elements, one

  on the other. The components which correspond to those already de-

  crits have the same references supplemented by the suffix

  "e". In the description given below, we will limit ourselves to

  discuss the differences from the embodiment of

Figure 6.

  In the embodiment of FIG. 7, the first bearing 144e is moved radially outwards where it bears against a peripheral shoulder 160e. In the inner radial zone, that is to say at the place where the screws 56e are located, there is provided a friction ring 162e subjected to

  the preload of a spring for example a Belle- spring

  city 164th and pressed against the first disc-shaped element 24th so that in the contact area of the ring

  friction 162e with the disc-shaped element 24e, it

  generates friction braking force. The 166th heads of

  56th screws enter the 168th cavities of the fric- ring

  tion 162e provided for heads. The 168th cavities have a certain peripheral length, so that the 166th heads

  can move freely over a certain peri-

  spherical in the 168th cavities without coming to bear against the ends of these cavities. If, however, there is excessive relative rotation between the first damping element 12e and the second damping element 14e, which may be the case when maximum torques occur, then the heads

  166e come to rest against the surfaces limiting the cavi-

  tees 168e in the peripheral direction and thus drive the friction ring 162e in the peripheral direction. As

  already indicated, this creates a damping force of friction

  which thus contributes to the amortization of the maximum torques

  mum. The torsional oscillation damper 10e shown in FIG. 7 thus comprises a sintering installation at

  delay effect which does not work for low rotation angles

  but which when a certain angle of rotation is reached acts and participates in the damping of the couples

  maximum by creating a friction force.

  Figure 8 shows a development of the embodiment shown in Figure 6 and Figure 7. The

  components which correspond to the components already described above

  above as to their construction and their function bear the same references with the addition of the suffix "f ,. For example when using the torsional oscillation damper 10f according to the invention as a second flywheel for a clutch with vehicle friction

  automotive, the first damping element 12f is connected so-

  in rotation with the crankshaft and the second element

  shock absorber 14f is connected by a friction clutch

  automobile vehicle, provided on the flywheel 52f, in the engaged state, rigidly and integral in rotation with the input shaft of the gearbox. If there is a slight offset or slight tilting of the axis between the crankshaft and the input shaft of the gearbox, or if during the operation of the internal combustion engine, the crankshaft is deformed due to action points

  connecting rods generates a nutation movement of the crankshaft,

  it can also result in a nutation movement of the first and / or second damping element 12f, 14f or else to a radial offset of these two components. This results in an excessive load of the bearings of these two components which due to the relative movement which occurs only for a limited angle of rotation between these two components, are often insufficiently greased. This is why in the embodiment of FIG. 8, the two bearings 144f,

  146f create the possibility for the first depreciated element

  12f and the second damping element 14f, to carry out

  one with respect to the other a movement of nutation. For this-

  la, the two bearings are constituted by bearing rings with elastic deformation which have, as shown in FIG. 8,

  an essentially V-shaped section.

  tilting ment of the two damping elements 12f, 14f

  relative to each other, this results in a deformation

  elastic tion of the two bearings 144f, 146f, that is to say the bearing rings themselves; this avoids excessive stress on the bearings. The prestressing spring 152f is also relatively hard

  weak to allow such a nutation movement to be followed while retaining its prestressing effect. To support the possibility of nu-

  tation, the flywheel 52f by which the second damping element 14f is supported on the bearing 146f, at a surface of

  170f convex bearing. This realization can produce a mo-

  bearing bearing in case of nutation movement, also

  ment in the bearing zone of the flywheel 52f on the bearing 146f and this rolling movement discharges the bearing even more. Similarly, the hub elements 140f, 142f have in their radially outer zone forming the ramp surface areas 74f, convex surfaces 172f, 174f in longitudinal section; in this case also in the event of a relative tilting of the first element with respect to the second damping element 12f, 14f, there is a movement of

  bearing on the respective support element 42f.

  Figure 9 shows another alternative embodiment.

  tion of the torsional oscillation damper according to the invention. The components that correspond to the components

  already described above bear the same complete references

  with the suffix "g". The following description is limited to

  ra to the essential constructive differences of this

variant.

  In the embodiment of Figure 9,

  the hub element 50g again comprises a first part

  58g hub tie as well as a second radial part provided-

  inside. This second part is connected to the flywheel 52g by bolts 56g connected to the second hub part 54g. Between the first and second hub parts 58g and 54g, there is a 180g friction clutch. The clutch

  friction 180g includes two friction rings for

  friction clutch 182g applied against the two axial faces of the radial flange 64g of the first hub part 58g. These friction clutch friction rings 182g are subjected to an axial preload of respective force accumulators, for example Belleville springs 184g;

  the latter lean against respective radial projections

  tives of the second hub part 54g or of an intermediate ring part 186g connected essentially so

  secured to the hub portion 54g and thereby pressing the

  clutch friction rings 182g against the radial flange 64g. Belleville 184g springs can act against the 54g hub part or against the intermediate ring part

  186g, either by friction, or by being joined together.

  The friction clutch 180g has, as already indicated in connection with FIG. 5, a damping effect to absorb the maximum torques. In the event of maximum intensity torque induced in the torsional oscillation damper and which

  could damage the components of this or the system

  drive tem, the adjustment of the sliding torque of the friction clutch 180g allows the sliding of the first damping element 12g and the first hub part 58g

  compared to the second 54g hub part as well as the

  lantern of inertia 52g. Due to this possible slip, the maximum torques are not transmitted by the shock absorber

of torsional oscillations 10g.

  FIG. 9 shows that the grease chamber 94g is closed in a leaktight manner on the right side of the figure by a sealing ring 154g subjected to the preload of a

  Belleville spring constituting a 156g force accumulator.

  The sealing ring 154g is thus applied against the

  186g intermediate ring tie. We see in Figure 9 that

  188g friction system acting between the second part

  54g hub tie and the first 12g damper element, is

  made with a friction ring and a pre-

  drag. This 188g friction installation generates at its

  turn a friction force independent of the angle of rotation

  tion and participating in the damping of torsional oscillations.

  The 184g friction clutch is not required-

  ment made symmetrically as shown in Figure 9. One can for example consider one of the friction rings and provide prestressing by the other friction ring alone. It is also possible to envisage an embodiment with several friction surfaces in parallel in the manner of a flap clutch, if the damper

  torsional oscillation is intended for example for char-

important ages.

  Figures 10 to 15 show different possibilities

  lites of realization of shock absorbing spring devices, ensuring the load damping function and applicable

  at the first shock-absorbing spring installation. Thus, Figure 10 shows in its left part, essentially the

  structure of the spring shock absorber device 38 already shown in FIG. 1 comprising two shock absorber springs 40. These two springs are supported by the support elements 44 in their end zone located in the peripheral direction, each time against parts

  support 36 of the first damping element 12. As this ap-

  appears in Figure 11, the support elements 36 have a body

  192 comprising bearing surfaces 190 essentially cir-

  rings to bear against the respective support pieces 36; two spring elements 194, 195 start from this body 192. Between these elements, there is a section cavity

  essentially circular to receive and guide the

  damped spring mites 40. The surface segment

  sliding 46 is provided on the spring 194 for the sliding

  ment on the sliding surface 34; on the spring 196, the driving surface area 76 has been produced against which the respective ramped surface area 74 of the second damping element 14 can bear. It is clear that both the sliding surface segment that the drive surface area 76 can extend to

  level of the body 192. The support element 42 is made of pre-

  plastic material because of the sliding properties

  and the ease of manufacture it must present. As FIG. 10 also shows, between the opposite ends of the shock-absorbing springs 40, a shoe 44 is provided which, due to the straight structure of the

  shock absorber springs 40 in the form of coil springs

  compression dales, provides for compression of the device

  spring shock absorber 38, a significant force deviation-

  in the peripheral direction. The right half of FIG. 10 shows a variant embodiment of a spring damping device, in particular an alternative embodiment at the level of the pad. The components which correspond to the components already described above have the same references supplemented by the suffix "h". In the right half of FIG. 10 and in the embodiment shown in FIG. 12, the shoe 44 of the left half is replaced by an intermediate element 44h which is guided without friction in the peripheral direction. For this and as it appears in FIG. 12, in the peripheral zone, between the cylinder-shaped segment 26:15 and the second disc-shaped segment 28h, there is an annular volume 200h receiving a support ring 202h having

  movement play both radially outward and radially

  inwardly. The support ring 202h carries the respective intermediate elements 44h for the different

  38h damping spring devices fixed by bou-

  lons 204h. The 44h intermediate elements have essential-

  a configuration in S or Z and extend from the volume

  200h ring finger in the area in which the resources are located

  shock absorbers 40h. As in general, we have

  several shock-absorbing spring devices 38h equidistant in the peripheral direction, that is to say that there are preferably at least three shock-absorbing spring devices

  with a peripheral interval of 120 each time, the ele-

  intermediate elements 44h connected integrally to the support ring 202h have a self-centering function for the assembly

  formed by the support ring 202h and the intermediate elements

  diaries 44h. This is mainly due to the fact that the different

* 40h shock absorber springs of the torsion damper

  are distributed substantially tangentially to a circle

  turning the axis of rotation A and thus their end zone generates a force component directed radially outwards, which is also transmitted to the different

  intermediate elements 44h. Due to the symmetrical realization

  these forces directed radially outwards are

  compensate each other, so that the intermediate ring

  diary 202h is worn or guided in rotation without pressing any assembly in the annular volume 200h. Such an embodiment is particularly advantageous in the case of dry torsional oscillation dampers, because at least at the level of the intermediate elements 44 h, this allows

avoid friction.

  As shown in Figure 12, the cylindrical segment 26h and the second disc-shaped segment 28h are connected to each other by a weld; it is also possible to rivet them, to screw them or to use a similar connection means. The intermediate elements 44h and the support ring 202h are preferably produced in the form of sheet metal parts for reasons of cost. We can

  also consider a realization in plastic material.

  Figures 13 and 14 show a variant of

  realization of the support ring with the intermediate elements

  diaries. The components which correspond to those already described

  above bear the same references supplemented by the suf-

fixed "i".

  In this embodiment, the support ring

  202i is made in one piece with the inter-

  mediaries 44i and is located radially substantially in the

  area in which the intermediate elements are also located

  diaries. This embodiment has the advantage of a construct-

  very compact; for example the support ring 202i with the intermediate elements 44i can be made of plastic by injection. In the same way, we can

  also consider a metal realization.

  The torsional oscillation damper according to the invention in principle also allows an embodiment in which the various shock-absorbing spring devices each time comprise a single damping spring. Such an embodiment is represented in the left half at the top of FIG. 15. The components which correspond to the components

  already described above bear the same references with ad-

  joining the suffix "k". In this type of embodiment, the shock spring 40k of the shock spring device

  38k is represented schematically outside in the par-

  left tie in the relaxed state, with an essential configuration

  partially rectilinear for a helical compression spring. However, the spring is then mounted in the 10k torsional oscillation damper, so that

  as also appears in the left half of the fi-

  gure 15, the spring is slightly bent. This is due to the fact that the respective bearing surfaces 210k of the bearing elements 42k or 212k comprise an intermediate element 44k having, with respect to the rectilinear embodiment of the damping spring 44k in the unloaded state, an angle of inclination

  respective (a and A). It should be noted that this realization

  inclined position of the bearing surfaces is possible at the same time

  in the embodiment mentioned above of a device for res-

  38k shock absorber output with a single 40k shock absorber spring than in an embodiment with several shock absorber springs and

  in addition to the intermediate elements 44k.

  This inclined arrangement of the support surfaces 210k, 212k means that, first of all in the unloaded state,

  shock absorber springs 40k are more strongly recommended

  traints on the radially inner side than on the radially side

  outside. As compression increases, the area

  dialement exterior is more strongly compressed, so that in the state of maximum compression, the shock absorber springs k are in the regularly compressed state represented in the upper left half of figure 15. We arrive

  thus to a spring characteristic varying gradually-

  ment in the different shock spring systems 38k which use the maximum possible deformation stroke for the different springs 40k. The angles (a and 3) are not

  not necessarily equal. Furthermore, as it appears on the left

  che in FIG. 15, it is possible to have a stepped embodiment of at least one of the bearing surfaces 210k, 212k, so that the radially inner zone of the shock-absorbing springs 40k is also more strongly prestressed in the unloaded state than the radially outer area. The stepped shape can be

  chosen so that in the no load state, the radially ex-

  40k springs is essentially not pre-

  drag and that it participates in the damping only as a function of the increasing relative rotation, by pressing against the radially external zone, receding in the direction pe-5 ripherique. It should be noted that instead of the stepped construction, it is also possible to provide an essentially rectilinear surface arranged at an angle. Figure 15 shows in its right half, another alternative embodiment of a damping device with

  spring. The components which correspond to those described above and which correspond to them by their functioning

  try the same references supplemented by the suffix "1". In the embodiment of Figure 15

  (right half), the supporting elements 421 have no lan

  spring watch or the like, but they essentially constitute a straight bearing surface for the shock-absorbing springs 401. The shock-absorbing spring devices 381 each time have only one shock-absorbing spring

  which in the uncharged state is preferably pre-bent. The res-

  shock absorbing spell 401 rests again by the opposite ends in the peripheral direction against the respective support elements 421 and thus against the support parts

  361 of the first damping element 121. In their radiating zone

  Lement exterior, the shock absorber springs 401 are applied against a spring cup 2201 which at the same time ensures the slip of the sliding surface 341 for the support elements 421. By the support of the shock absorber springs 401 in their radially exterior zone, an additional friction component is introduced which contributes to damping the oscillations. As the force of application of the damping springs 401 against the spring cup 2201 on the one hand increases with increasing compression, that is to say the relative angle of rotation and on the other hand with the increase in the speed of rotation, i.e.

  centrifugal force, we have a friction component which

  depends on both the torque to be transmitted and the instantaneous speed of rotation. The embodiment shown in

  half of Figure 15 is particularly advantageous for receiving

  to see or to decouple important couples. The arrangements

  shock-absorbing spring elements 381 can have an angular length which corresponds practically to 180, so that the shock-absorbing spring installation 201 comprises two such shock-absorbing spring devices 381. It is also possible to envisage any other angular length.

  Massive production of support elements 421

  without the respective spring rings leads to them

  these allow more normal forces to be received

  tes, i.e. a stronger corner effect for

induction of couples.

  To avoid wear of the sliding surfaces 341 during operation, the spring cup 2201 has at least at its sliding surface 341 and the bearing surface for the damping spring 401, an area made of a treated material. This can also be provided in all the embodiments already described in which the cylindrical segment of the first damping element can

  be made at least in the area forming the covering surface

  smoothing, in a treated material or have an insert or a

coating of treated material.

  The embodiments described above of the torsional oscillation damper according to the invention make it possible to envisage numerous modifications. Thus it is for example possible to produce the second damping element in its peripheral surface area in a polygonal shape and then each time in each corner area, there are surfaces in the form of a ramp. As a variant of the embodiments described above for which there is

  in each corner area a ramp-shaped surface only-

  ment for a support element, it is also possible to produce the second damping element so that in a corner area, in each peripheral direction, a ramp surface is formed each time so that it thus serves each

  times according to the relative rotation between the first and the second

  cond damper element of the corner area to the drive of different directly adjacent support elements in the

  peripheral direction for the various devices to be

  shock absorber. However in general in this embodiment, there is a dry run which does not exist in the embodiments shown during the relative rotation between the first and the second damper part5. This means that the different corners of the polygonal peripheral shape must first of all rotate within a predetermined angular range until it comes to bear against a respective support element. In addition, it is also possible to produce the torsional oscillation damper according to the invention with first and second damping elements which, in their respective zone provided for

  the transmission of the torque, are not radially opposite but are axially. Thus each damping element has a surface facing the other damping element 15 which is essentially perpendicular to the axis of rotation.

  tion. One of the damping elements then comprises

  axial projections which also form supporting parts

  tre which are fitted with shock absorbing spring devices and which are supported each time in the peripheral direction

  at their two end zones.

  The other damping element comprises, at its axial surface, axially projecting drive elements which can be formed by axially directed ramp surfaces. In case of relative rotation, these

  ramp-shaped elements can then cause the

  shock absorber spring by means of supporting elements

  respondents and compress it. In this case too, the same

  effect that the one generating the friction force can be ob-

  held by a ramp-shaped embodiment of the projecting surfaces on the other damping element. In addition, in such an embodiment, external support means are required in the radial direction avoiding any radially escaping

  towards the outside of the shock-absorbing spring device.

Claims (28)

R E V E N D I C A T I ON S   1) Torsional oscillation damper in particular for damping torsional oscillations produced in the transmission line of a motor vehicle comprising: - a first damping element (12), a second damping element (14) which can rotate around an axis of rotation (A) relative to the first damping element (12), - a first damping spring installation (20) which couples the first and the second damping element (12, 14) for the transmission of the torque,   - the first shock-absorbing spring installation (20) includes   providing at least one shock-absorbing spring device (38) extending approximately in the peripheral direction with at least one shock-absorbing spring (40), - on a shock-absorbing element (12) of the first and second damping element (12, 14), there are support means (36) for at least one shock-absorbing spring device (38), against which at least one device is supported   shock absorbing spring at its end zones   pectives, substantially in the peripheral direction, by a support element (42) provided in each end and,   - on at least one damping element (12) for each element   support element (42), there is a sliding surface (34) along which the corresponding support element (42) can slide in the peripheral direction, and   - in addition on the other damping element (14) among the first-   mier and the second damping element (12, 14) are provided with drive means (74) associated with each element   support (42) by which, on the occasion of a movement   lative between the first and the second damping element (12, 14), the associated bearing element (42) can be pushed for a sliding movement along the associated sliding surface (34) on a damping element (12 ) and towards the sliding surface (34), characterized in that at least at the level of the sliding surface (34), it is   provided with at least one grease chamber (94) sealed tight   outwardly and containing grease (96) 2) Torsional oscillation damper according to claim 1, characterized in that at least one damping spring (40) is provided at least per zone in the chamber grease (94) and enters the grease (96).   ) Torsional oscillation damper according to one conch of claims 1 and 2,   characterized in that the grease chamber is formed by:   - A first segment (24) in the form of a disc extending es-   substantially radially and belonging to the first damping element (12), - a cylindrical segment (26) extending essentially   axially, and adjacent to the first dis-shaped segment   that (24) at its radially outer zone, - a second segment (28) preferably in the form of a ring of the disc, extending essentially radially like a disc, on the cylindrical segment (26) by its end   opposite the first disc-shaped segment (24), so   adjacent section with its radially outer end zone   superior, extending essentially radially.   4) Torsional oscillation damper according to the claim   tion 3, characterized in that the sliding surface (34) is designed as   a cylindrical segment (26) at its peri-surface indoor sphere.    ) Torsional oscillation damper according to claim 3 or 4, characterized in that - the second damping element (14) is rotatably mounted by   a bearing device (16) on the first damping element   weaver (12) and / or a component (18) integrally connected thereto and the bearing device (16) forms a first sealing device for the grease chamber (94) relative to   an axial side of the second damping element (14).   6o) Torsional oscillation damper according to the claim tion 5, characterized in that   it further comprises a second sealing device (90, 92; 154d, 156d) provided between the second segment (28) in the form of a disc and the second damping element (14), on its au- be on the axial side.   7) Torsional oscillation damper according to one conch of claims 1 to 6,   characterized in that the first disc-shaped segment (24) and / or the cylindrical segment (26) preferably form an integral part of the first disc-shaped segment (24) and / or the second disc-shaped segment (28 ) and / or the second damping element (50d), comprising at least one sheet metal part (140d, 142d)   preferably shaped by deep drawing.   8) Torsion oscillation damper according to the preamble of claim 1, if necessary in combination with one or more of the preceding characteristics, characterized by an overload protection installation (26c,   vs; 162nd; 180g) to absorb the maximum torques to be trans-   put through the torsional oscillation damper.   9) Torsional oscillation damper according to the claim   tion 8, characterized in that the overload protection installation (26c, c; 180g) comprises at least one sliding clutch device. 10) torsional oscillation damper according to claim 9, characterized in that the overload protection installation comprises   a friction clutch device (26c, 130c) acting in   two components of the first damping element (12c) and / or a friction clutch device (180g) acting   between two components of the second damping element (14c). -   11) Torsional oscillation damper according to one conch of claims 9 or 10,   characterized by at least one slip clutch device (26c, 130c) having an annular slip member (130c) mounted   turning on the damping element (12c) and attacking it   this by friction, and this annular element has the surface   sliding (34c) and the support means.   12) Torsional oscillation damper according to one conch of claims 8 to 11, characterized in that   the overload protection installation (162e) includes   takes an installation generating a friction force (160e) acting between the first and the second damping element   (12e, 14e) or the components integral with these, and gener-   rant as the relative angle of rotation increases   tive, an increasing friction force between the first and the   second damping element (12th, 14th).   13) Torsional oscillation damper as claimed cation 12, characterized in that   the installation generating a friction force (160th) does not   hardly any friction force up to an angle   relative rotation constituting a threshold and when exceeding   ment of this relative angle of rotation constituting a threshold, it generates an essentially constant friction force or   increasing with the relative angle of rotation.   14) Torsional oscillation damper according to the preamble of claim 1 and the case in combination with one or more of the preceding characteristics, the second damping element (14f) being rotatably mounted by means of a bearing device ( 144f, 146f) on the first damping element (12f) or / and on components (18f) integral with it, characterized in that the bearing device (144f, 146f) is produced so that the first and the second element shock absorber (12f, 14f) allows at least one tilting movement and / or one   sliding movement in the radial direction.    ) Torsional oscillation damper as claimed   cation 14, characterized in that the bearing device (144f, 146f) comprises at least one bearing component (144f, 146f) elastically deformable from   preferably plain bearing components.   16) Torsional oscillation damper as claimed   cation 15, characterized in that the bearing device (144f, 146f) comprises bearing components (144f, 146f) acting between the first and the second   damping element (12f, 14f) essentially in the direction   tion and a component acting between the first and the second damping element essentially in the radial direction.   17) Torsional oscillation damper according to one conch of claims 14 to 16,   characterized in that the second damping element (14f) has a surface of   convex bearing (170f) to bear against the device bearing tif (146).   18) Torsional oscillation damper according to one of claims 14 to 17, characterized in that   the drive means (74f) comprise on the other element   shock absorber (14f) each time a driving surface convex (74f).   19) Torsion oscillation damper according to the preamble of claim 1 and the case in combination with one or more of the preceding characteristics, characterized in that - at least one spring damping device (38) comprises at least two damping springs (40) and - at least the two damping springs (40) are supported by   their neighboring end zone against an intermediate element   diary (44) which can move in the peripheral direction   risk with respect to a damping element (12).    ) Torsional oscillation damper as claimed cation 19, characterized in that   the intermediate element (44) comprises a sliding element   ment (44) sliding on the sliding surface (34).   21) Torsional oscillation damper as claimed cation 19, characterized in that   the intermediate element (44h; 44i) is essential mobile-   frictionless in the peripheral direction relative to   to a damping element (12h; 12i).   22) Torsional oscillation damper according to one   conch of claims 19 to 21 comprising several provisions   spring shock absorbers (38h; 38i) distributed in an essentially equidistant manner in the peripheral direction   and the respective intermediate elements (44h; 44i) for the various spring damping devices (38h; 38i) are mounted on a support ring (202h; 202i) rotating5 relative to a damping element (12h; 12i).   23) Torsional oscillation damper according to the preamble of claim 1 and if necessary in combination with one or more of the preceding characteristics, characterized by at least one other spring damper installation (22; 122a) which is mounted way to cooperate in series with the   first installation of spring shock absorber (20; 20a).   24) Torsional oscillation damper as claimed   cation 23, characterized in that at least the other spring damping installation (22; 122a) comprises at least one spring damper device   with at least one damping spring (72; 124a).    ) Torsional oscillation damper as claimed   cations 23 or 24, characterized by at least one other spring shock absorber installation (22) comprising a torque transmission coupling between two components rotating relative to each other of the first shock absorber element and / or between two components (58, 54)   rotating relative to each other of the second damping element weaver (14).   260) Torsional oscillation damper according to one conch of claims 23 to 25,   characterized by a friction clutch (102a) associated with the torsional damper oscillator (10a) with a clutch disc (11Oa), this clutch disc (11Oa) comprising at least one other damping installation with spring (122a) cooperating between two components (114a, 116a, 120a) capable of   turn relative to each other and belonging to the clutch disc (11Oa).   27) Torsional oscillation damper according to one   conch of the preceding claims,   characterized in that the first shock-absorbing spring installation (20) and / or the   if necessary at least one other spring-loaded installation   weaver include end stop means (30,   ; 82, 84; 86, 88) to limit the relative angle of rotation   component rotating relative to one another 28) Torsional oscillation damper according to the preamble of claim 1 and if necessary in combination with one or more of the preceding characteristics, the surface   sliding (34a) being provided on a peripheral surface   that interior of a cylindrical segment (26a) extending es-   axially and belonging to a damping element (12a), characterized by axial fixing means-support element (128a, 130a) acting between a damping element (12a) and each element support (42a).   290) Torsional oscillation damper as claimed   cation 28 or the preamble of claim 28, characterized in that it comprises at least one shock-absorbing spring device (38a) with at least two shock-absorbing springs (40a), the two neighboring end regions of which move relative to   one of the damping elements, in the peripheral direction   preferably by resting on the intermediate sliding element on the sliding surface and axial fixing means - intermediate element are provided for the intermediate element.    ) Torsional oscillation damper as claimed   cation 28 or claim 29, characterized in that the means of axial fixing of the support element (128a, 130a) and / or where appropriate the means of axial fixing of   the intermediate element include on an element of the over-   sliding face (34a) and of the support element (42a) or an intermediate element, a peripheral groove (130a) and on each other element, a projecting fixing zone   (128a) entering the peripheral groove (130a).   31) Torsional oscillation damper according to one conch of claims 28 to 30,   characterized in that - a damping element (12a) comprises a segment (24a) in   disc shape which extends mainly in the direction   tion radially and which is connected in a radially ex-   prior to a cylinder-shaped segment (26a) and is provided on a first axial side of each support element (42a) and - the other damping element (14a) comprises a disk-shaped segment (52a) s' basically extending into the   radial direction and which is in a radial area-   outer outer side of each element support (42a).   32) Torsional oscillation damper as claimed   cation 31, characterized in that between the disc-shaped segment (52a) of the other damping element (14a) and each support element (42a), there is a   predetermined axial distance (D).   33) Torsional oscillation damper according to the preamble of claim 1 and, where appropriate, in combination with one or more of the preceding characteristics, characterized in that   at least one damping spring (40k) has a characteristic   Variable spring ristics with increasing relative rotation between the first and the second damping element (12k, 14k).   34) Torsional oscillation damper as claimed   cation 33, characterized in that at least one damping spring (40k) has, in the basic state, an approximately rectilinear configuration and in the assembled and unloaded state of the damper   torsional oscillations (10k), it is more strongly pre-   constrained in the spring area located radially inside that in the spring area located radially to outside.    ) Torsional oscillation damper according to one conch of claims 33 or 34, characterized in that   at least one shock absorbing spring (40k) is prestressed   essentially identical, in the essentially compressed state and at most, in its radially outer zone   and in its radially inner zone.   36) Torsional oscillation damper according to one conch of claims 33 to 35,   characterized in that at least one damping spring (40k) has in its state of   essentially maximum compression, an essential configuration partially straight.   37) Torsional oscillation damper according to one conch of claims 33, 36,   characterized in that at least one damping spring (44k) bears at least in one of its end zones against a bearing surface   (212k) with a radially outer support area   bent relative to its radially inner bearing zone,   in the peripheral direction, for at least one of the zo-   end nes of at least one shock spring stroke k. 38 0) Torsional oscillation damper according to the preamble of claim 1 and if necessary in combination with one or more of the preceding characteristics, characterized in that - at least one damping spring (401) is preferably pre-bent and s extending from the peripheral direction and   - radial support means (2201) are provided which support-   at least one shock absorbing spring (401) in its narrow zone   outer dial preferably over its entire length, radially outward.   39 0) Torsional oscillation damper as claimed cation 38, characterized in that   the radial support means (2201) consist of an over- sliding face (341).    ) Torsional oscillation damper according to one conch of claims 38 or 39,   characterized in that the radial support means (2201) comprise a path of treated support.   41) Torsional oscillation damper according to one conch of claims 38 to 40, characterized in that   at least one shock-absorbing spring device (38k, 381) comprising   takes only one damping spring (40k, 401).   42) Torsional oscillation damper according to one of the claims 1 to 41,   characterized in that - the support element (42) has a substantially wedge-shaped shape which narrows in the peripheral direction and a sliding surface segment (46) applied against the sliding surface (34) in one piece damping element (12) for the support element (42) forms a first corner surface and a drive surface (76) provided for bearing against the respective drive means (74) forms a second surface corner and   - the drive means (74) include a sur-   face in the form of a drive ramp (74) at least per segment, parallel to each drive surface (76) 43) Torsional oscillation damper according to claim 42,   characterized in that the sliding surface segment (46) has a surface cone at least approximately adapted to the peripheral contour of the sliding surface (34).